EP0994275A1 - Courroie de transmission, élément pour celle-çi et ensemble l'utilisant - Google Patents

Courroie de transmission, élément pour celle-çi et ensemble l'utilisant Download PDF

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Publication number
EP0994275A1
EP0994275A1 EP98203409A EP98203409A EP0994275A1 EP 0994275 A1 EP0994275 A1 EP 0994275A1 EP 98203409 A EP98203409 A EP 98203409A EP 98203409 A EP98203409 A EP 98203409A EP 0994275 A1 EP0994275 A1 EP 0994275A1
Authority
EP
European Patent Office
Prior art keywords
profile
belt
contact
drive belt
contact surface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP98203409A
Other languages
German (de)
English (en)
Other versions
EP0994275B1 (fr
Inventor
Paulus Maria Smeets
Johannes Hendrikus Lith
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Transmission Technology BV
Original Assignee
Van Doornes Transmissie BV
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Van Doornes Transmissie BV filed Critical Van Doornes Transmissie BV
Priority to DE69818466T priority Critical patent/DE69818466T2/de
Priority to EP98203409A priority patent/EP0994275B1/fr
Publication of EP0994275A1 publication Critical patent/EP0994275A1/fr
Application granted granted Critical
Publication of EP0994275B1 publication Critical patent/EP0994275B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
    • F16G5/00—V-belts, i.e. belts of tapered cross-section
    • F16G5/16—V-belts, i.e. belts of tapered cross-section consisting of several parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
    • F16G5/00—V-belts, i.e. belts of tapered cross-section
    • F16G5/16—V-belts, i.e. belts of tapered cross-section consisting of several parts
    • F16G5/163—V-belts, i.e. belts of tapered cross-section consisting of several parts with means allowing lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/24—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using chains or toothed belts, belts in the form of links; Chains or belts specially adapted to such gearing

Definitions

  • the present invention relates to, inter alia, a drive belt for a continuously variable transmission having belt discs having an at least partially conical contact surface for enclosing a drive belt between pairs of said discs, which drive belt to this end comprises one or more transverse elements provided with converging side faces intended to come into contact with the contact surface of a belt disc and wherein one or more side faces possess a surface which has protuberances providing a profile, which surface has therein contact faces, defined by the protuberances, for coming into contact with the contact surface of a belt disc.
  • a drive belt of this type also referred to as a belt, is disclosed in European Patent Application 0.381.258.
  • the elements have a predetermined profiled contact surface having protuberances formed by ridges and having recesses formed by grooves.
  • the width of the contact face of a ridge, measured “in the profile” is at most 100 ⁇ m and the width of a groove is less than or equal to 300 ⁇ m, the grooves taking up at least fifty percent of the total surface in which they are present.
  • the drive belt operates together with a set of belt discs in combination with supplied oil, which inter alia serves to remove heat.
  • the ratio between the surface dimensions of protuberances and grooves is optimised with respect to the discharge of oil into the grooves and collection of oil in said grooves, in order to prevent slip between drive belt and belt disc.
  • the known construction has the disadvantage that when the transmission is taken into use for the first time damage to the pulley and belt, or breakage of the belt, can occur initially.
  • the aim of the present invention is at least advantageously to overcome or substantially to prevent this phenomenon, at least to obtain an improved profile, preferably a profile shaped such that, in order to prevent the above mentioned problems, optimum account is taken of physical phenomena which arise between drive belt and belt disc during running in.
  • this is achieved when the profile is shaped such that on cross-sectioning parallel to the side face concerned or after wear of the profile at or down to a level located at least thirty percent and at most seventy percent of the profile height beneath the initial profile height, the surface area effectively available for coming into contact with the contact surface of a belt disc lies within the range of forty to sixty percent with respect to the dimensions of the side face in which the contact faces are present.
  • a construction of this type advantageously provides a possibility for running in the drive belt and provides an advantageous shape for the protuberances which, whilst retaining advantageous ratios with respect to discharge of oil into the grooves and collection of oil in said grooves, is optimised with respect to correct and advantageous running-in wear and which prevents damage and has a beneficial effect on the period for which the belt can be put under load.
  • Running-in in accordance with the invention is possible by means of wearing down profile sections in the outermost layer of the profile to a depth of, for example, approximately 10 ⁇ m, in which layer the proportion of the profile that acts as a bearing surface is small, and thus the possibility of wear is high.
  • Such an optimum possibility for initial wear prevents elements of the drive belt eating into the contact surface of the pulley, or giving rise to irregularities, such as scores, therein, during running-in of a belt and pulley combination.
  • This possibility arises, for example, as a consequence of variation in width of successive elements in a belt, or the inequality therein with respect to an imaginary plane of symmetry between two pulley discs, or as a consequence of variation in the angle of the flanks of the elements.
  • Such an element can be forced radially outwards under the pressure of the pulleys so that an adversely high tension and a local adversely high load on an innermost band of a composite band of the drive belt would be created.
  • the possibility for initial wear created according to the invention thus also leads to optimum seating of a belt/pulley combination and also prevents belt breakage or damage to the pulley on running-in a relatively wide element between two pulley discs.
  • the construction according to the invention also has the advantage that the contact surface is initially minimal but, as a result of the preferably sinusoidal shape, relatively rapidly decreases by wear in a controlled manner until an equilibrium situation is reached in which further wear is negligible.
  • the shape proposed according to the invention also has the advantage that the proportion of the contact surfaces which act as bearing surfaces adjust in an optimum manner in a belt/pulley combination to possibly .varying values in hardness of the material of either the disc or the elements, or to a possibly varying composition of the material thereof.
  • Japanese Patent Application 58-189587 discloses an element which has a contact surface that possesses an infinite number of minute projections, apparently present in stochastic distribution.
  • the initial contact of said surface is at least twenty percent in order to prevent slip and wear.
  • the aim in the present invention is for a slight but controlled degree of initial wear.
  • the document provides no information on possible dimensions or tolerances of the shape of the projections.
  • the Derwent abstract of Japanese Patent Application 3-185686 discloses a contact surface having micro-irregularities obtained by so-called shot blasting. To increase resistance to wear, the rough surface thus obtained is smoothed until a specific proportion of the projections acting as bearing surfaces is reached.
  • the present invention teaches that initial wear of the elements must be achieved during running-in of a belt in order thus to prevent shock loading, which can arise as a consequence of an unfavourable sequence of successive elements in a belt and of elements varying in width within a tolerance.
  • the drive in FIGURE 1 comprises a pair of slightly conical belt discs 1, 2 with a drive belt 3 fitted between them.
  • the drive belt is provided with a support 7, on which the transverse elements 6 are movably mounted.
  • One embodiment of such a transverse element is shown in FIGURE 2.
  • the transverse element 6' concerned is provided with a recess 13 for accommodating a support which, for example, can consist of a bundle of metal bands. Said recess 13 can be closed at the top by means of a locking pin 10, which can be fitted in the bores 11 and 12 of the transverse element 6'.
  • Another embodiment of a transverse element is shown in FIGURE 3. In this case the transverse element 6 concerned has a pair of recesses 14 in which a support 7 can be accommodated.
  • the support 7 is usually formed by a bundle of continuous elements, such as flat, flexible metal bands, placed one on top of the other.
  • the transverse elements, 6 and 6' respectively are provided with converging side faces 8 which are able to engage on the respective conical contact surfaces 4 and 5 of the belt discs 1 and 2, which are usually arranged at an angle of approximately 11°.
  • an oil film can be formed between the contact surfaces 4 and 5 on one side and the side faces 8 on the other side, as a consequence of which the drive belt is able to slip with respect to the belt discs 1 and 2 and as a result of which the transmitted torque decreases.
  • the efficiency of the transmission will decrease as a result and excessive wear can occur.
  • the side faces 8 and/or the contact surfaces 4, 5 must be discontinuous or roughened.
  • FIGURES 4a and 4b illustrate the transverse elements 6 having side faces 8 provided with a profiled surface.
  • the profile is defined by recesses in the form of grooves 15, which are parallel or oblique with respect to the longitudinal direction of the support 7, between protuberances in the form of ridges 16, which likewise can run parallel or obliquely with respect to the support 7.
  • reference will always be made below to the grooved surfaces of the transverse elements; however, it will be clear that the same applies correspondingly to the contact surfaces 4 and 5 of the respective belt discs 1 and 2 and to profiles which are formed by gritting, shot blasting or shot peening.
  • protuberances for example formed stochastically as by shot blasting or formed in a predetermined manner and in this case with grooves or protuberances which, for example, are straight, oblique, stepped, curved or of some other shape.
  • FIGURE 5 is a cross-section of a groove profile known per se, at right angles to the contact surface 8 and in the lengthwise or depth direction thereof.
  • the profile comprises ridges 16, which have an effective width Ld, and grooves positioned between said ridges, said grooves having an effective width Lg.
  • the grooves act as a facility for receiving and removing the oil. It is desirable to remove oil rapidly so that there is no risk of an oil film being formed between the contact surfaces of transverse element and belt disc or, if an oil film has already been formed, to break this up and reduce it as quickly as possible.
  • the effective width Ld of the ridges must be sufficiently small, so that the oil has to be moved only over a limited distance before it is collected in the grooves.
  • the total groove surface that is to say also the groove depth h.
  • said groove depth is preferably within the range of 15-30 ⁇ m, so that there is a possibility of running-in or initial wear and that, on the one hand, even after running-in of the belt, or after wear of the side faces 8 of the elements, adequate groove volume is obtained, so that sufficient oil can be collected, and so that, on the other hand, the groove depth or the height of the protuberances or depth of the recesses is not so high that this causes failure of the protuberances.
  • Figures 7 and 8 show alternatives of novel profiles, formed in accordance with the insights on which the invention is based, for the side faces 8.
  • a good flow of the oil from a ridge 16 into the groove 15 is retained with these designs, so that a non-uniform flow with an undesirable pressure built-up is prevented with a relatively high degree of certainty.
  • a sinusoidal profile is preferably used according to the invention. This profile on the one hand complies with the concept on which the present invention is based, that some degree of wear of the flank profile is desirable, because the profile has an initially minimal contact surface so that initial wear proceeds rapidly and easily, whilst, on the other hand, an at least quasi-equilibrium situation, in which the proportion acting as bearing surface is approximately fifty percent, is reached relatively rapidly.
  • the proportion acting as bearing surface is the ratio of the surface area of the protuberances, or the surface area of all protuberances in a side face 8 which is effectively available to bear on a belt disc 1 and 2, to the total surface area in which the protuberances or recesses are accommodated, for example the surface area that is defined by the height and width of the side faces 8.
  • the sinusoidal profile also has the advantage that the recesses do not have any sharp corners which could cause damage to the disc during running-in and that the resistance to failure is relatively high. Nevertheless, a ridge 16 according to the invention viewed in cross-section can be completely triangular, although fractional smoothing of the protuberances can be employed in connection with the sharpness of the point.
  • FIGURE 9 illustrates the change in the average height h of the protuberance, plotted on the Y axis ("Y"), as a consequence of wear, as a function of the speed of revolution ("X") of the drive belt in a drive belt and belt disc unit according to Figure 1.
  • the profile according to the invention has been optimised for advantageous utilisation of the initial wear of the elements, which phase changes close to point Z, after a few tens of thousands to a few hundreds of thousands of complete revolutions of the belt, into a quasi-steady situation in which the degree of wear of the profile tends towards zero.
  • the shape of a protuberance developed according to the invention promotes very rapid seating of a combination of belt disc with drive belt, which is beneficial with regard to the period for which the belt can be subjected to load.
  • the shape according to the invention prevents clearing of oil to collection of oil in the grooves being adversely affected or the width of an element decreasing to such an extent that problems arise in relation to the margins for the distance between drive belt axis and element or between the belt disc 4, 5 and the bands 7.
  • a protuberance at the height at which quasi-stabilisation of wear is considered to take place or takes place, has a width which, viewed "in profile" in accordance with Figures 7 and 8, is at most approximately, that is to say plus or minus 10 percent, 13 ⁇ m, preferably approximately 8 ⁇ m.
  • the mutual spacing of the protuberances that is to say the centre-to-centre distance, must be approximately three times as great in this case.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmissions By Endless Flexible Members (AREA)
  • Pulleys (AREA)
EP98203409A 1998-10-12 1998-10-12 Courroie de transmission, élément pour celle-çi et ensemble l'utilisant Expired - Lifetime EP0994275B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE69818466T DE69818466T2 (de) 1998-10-12 1998-10-12 Treibriemen, Element dafür und mit diesem versehene Vorrichtung
EP98203409A EP0994275B1 (fr) 1998-10-12 1998-10-12 Courroie de transmission, élément pour celle-çi et ensemble l'utilisant

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP98203409A EP0994275B1 (fr) 1998-10-12 1998-10-12 Courroie de transmission, élément pour celle-çi et ensemble l'utilisant

Publications (2)

Publication Number Publication Date
EP0994275A1 true EP0994275A1 (fr) 2000-04-19
EP0994275B1 EP0994275B1 (fr) 2003-09-24

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EP98203409A Expired - Lifetime EP0994275B1 (fr) 1998-10-12 1998-10-12 Courroie de transmission, élément pour celle-çi et ensemble l'utilisant

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EP (1) EP0994275B1 (fr)
DE (1) DE69818466T2 (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL1017122C2 (nl) * 2001-01-16 2002-07-17 Doornes Transmissie Bv Dwarselement voor een drijfriem voor een continu variabele transmissie.
EP1199494A3 (fr) * 2000-10-19 2004-01-14 Honda Giken Kogyo Kabushiki Kaisha Courroie pour transmission variable en continu
NL1023667C2 (nl) 2003-06-16 2004-12-20 Bosch Gmbh Robert Metalen drijfriem.
WO2006065116A1 (fr) * 2004-12-17 2006-06-22 Robert Bosch Gmbh Procede pour former un element transversal pour une courroie de poussee d'une transmission a variation continue
WO2006068458A1 (fr) 2004-12-20 2006-06-29 Robert Bosch Gmbh Courroie d'entrainement pour une transmission variable en continu
WO2006135225A1 (fr) 2005-06-13 2006-12-21 Robert Bosch Gmbh Courroie de transmission pour transmission à variation continue et procédé de fabrication d’élément transversal pour ladite courroie de transmission
WO2007064206A1 (fr) 2005-12-02 2007-06-07 Robert Bosch Gmbh Courroie de transmission pour transmission à variation continue et élément transversal utilisé avec ladite courroie
US7261656B2 (en) * 2003-03-06 2007-08-28 Nissan Motor Co., Ltd. Metal V-belt
CN100346900C (zh) * 2002-07-03 2007-11-07 范多尔内斯变速器公司 用于连续可变传动装置的压带的横向元件的形成方法
NL1037483C2 (en) * 2009-11-19 2011-05-23 Bosch Gmbh Robert Push belt for a continuously variable transmission, comprising different types of transverse elements.
NL1039559C2 (en) * 2012-04-23 2013-10-28 Bosch Gmbh Robert Belt-and-pulley-type continuously variable transmission.
JP2021008909A (ja) * 2019-06-28 2021-01-28 ダイハツ工業株式会社 締付対象物の共回り抑制構造

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58189587A (ja) 1982-04-30 1983-11-05 株式会社東芝 異常音発生位置推定方式
JPS5997344A (ja) * 1982-11-22 1984-06-05 Toyota Motor Corp 金属ベルトの無端キヤリヤ押え駒製造方法
JPS6081537A (ja) * 1983-10-11 1985-05-09 Toyota Motor Corp 無段変速機用ベルトブロツク
JPS60136650A (ja) * 1983-12-22 1985-07-20 Taiho Kogyo Co Ltd ベルト式連続可変伝達機構
EP0381258A1 (fr) 1989-02-03 1990-08-08 Van Doorne's Transmissie B.V. Transmission comprenant une courroie et des poulies en "V"
JPH03185686A (ja) 1989-12-13 1991-08-13 Matsushita Electric Ind Co Ltd 摺動装置
JPH0510405A (ja) * 1991-06-28 1993-01-19 Toyota Motor Corp ベルト式伝動装置

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58189587A (ja) 1982-04-30 1983-11-05 株式会社東芝 異常音発生位置推定方式
JPS5997344A (ja) * 1982-11-22 1984-06-05 Toyota Motor Corp 金属ベルトの無端キヤリヤ押え駒製造方法
JPS6081537A (ja) * 1983-10-11 1985-05-09 Toyota Motor Corp 無段変速機用ベルトブロツク
JPS60136650A (ja) * 1983-12-22 1985-07-20 Taiho Kogyo Co Ltd ベルト式連続可変伝達機構
EP0381258A1 (fr) 1989-02-03 1990-08-08 Van Doorne's Transmissie B.V. Transmission comprenant une courroie et des poulies en "V"
JPH03185686A (ja) 1989-12-13 1991-08-13 Matsushita Electric Ind Co Ltd 摺動装置
JPH0510405A (ja) * 1991-06-28 1993-01-19 Toyota Motor Corp ベルト式伝動装置

Non-Patent Citations (4)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 17, no. 284 (M - 1421) 31 May 1993 (1993-05-31) *
PATENT ABSTRACTS OF JAPAN vol. 8, no. 210 (M - 328) 26 September 1984 (1984-09-26) *
PATENT ABSTRACTS OF JAPAN vol. 9, no. 223 (M - 411) 10 September 1985 (1985-09-10) *
PATENT ABSTRACTS OF JAPAN vol. 9, no. 300 (M - 433) 27 November 1985 (1985-11-27) *

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1199494A3 (fr) * 2000-10-19 2004-01-14 Honda Giken Kogyo Kabushiki Kaisha Courroie pour transmission variable en continu
WO2002061304A1 (fr) * 2001-01-16 2002-08-08 Van Doorne's Transmissie B.V. Element transversal destine a une courroie d'entrainement pour transmission a variation en continu
NL1017122C2 (nl) * 2001-01-16 2002-07-17 Doornes Transmissie Bv Dwarselement voor een drijfriem voor een continu variabele transmissie.
US7892126B2 (en) 2001-01-16 2011-02-22 Bosch Transmission Technology B.V. Transverse element for a drive belt for a continuously variable transmission
CN100346900C (zh) * 2002-07-03 2007-11-07 范多尔内斯变速器公司 用于连续可变传动装置的压带的横向元件的形成方法
US7261656B2 (en) * 2003-03-06 2007-08-28 Nissan Motor Co., Ltd. Metal V-belt
NL1023667C2 (nl) 2003-06-16 2004-12-20 Bosch Gmbh Robert Metalen drijfriem.
WO2004111490A1 (fr) 2003-06-16 2004-12-23 Robert Bosch Gmbh Courroie d'entrainement en metal
WO2006065116A1 (fr) * 2004-12-17 2006-06-22 Robert Bosch Gmbh Procede pour former un element transversal pour une courroie de poussee d'une transmission a variation continue
WO2006068458A1 (fr) 2004-12-20 2006-06-29 Robert Bosch Gmbh Courroie d'entrainement pour une transmission variable en continu
WO2006135225A1 (fr) 2005-06-13 2006-12-21 Robert Bosch Gmbh Courroie de transmission pour transmission à variation continue et procédé de fabrication d’élément transversal pour ladite courroie de transmission
WO2007064206A1 (fr) 2005-12-02 2007-06-07 Robert Bosch Gmbh Courroie de transmission pour transmission à variation continue et élément transversal utilisé avec ladite courroie
US20120277048A1 (en) * 2009-11-19 2012-11-01 Robert Bosch Gmbh Push Belt For A Continuously Variable Transmission, Comprising Different Types Of Transverse Elements
WO2011062480A1 (fr) 2009-11-19 2011-05-26 Robert Bosch Gmbh Courroie de poussée pour une transmission variable continue comportant différents types d'éléments transversaux
CN102667234A (zh) * 2009-11-19 2012-09-12 罗伯特·博世有限公司 包括不同类型的横向元件的用于无级变速器的推带
NL1037483C2 (en) * 2009-11-19 2011-05-23 Bosch Gmbh Robert Push belt for a continuously variable transmission, comprising different types of transverse elements.
US9133908B2 (en) * 2009-11-19 2015-09-15 Bosch Transmission Technology B.V. Push belt for a continuously variable transmission, comprising different types of transverse elements
CN102667234B (zh) * 2009-11-19 2015-10-14 罗伯特·博世有限公司 包括不同类型的横向元件的用于无级变速器的推带
NL1039559C2 (en) * 2012-04-23 2013-10-28 Bosch Gmbh Robert Belt-and-pulley-type continuously variable transmission.
WO2013159910A1 (fr) * 2012-04-23 2013-10-31 Robert Bosch Gmbh Transmission à variation continue du type à courroie et poulie
US9371902B2 (en) 2012-04-23 2016-06-21 Robert Bosch Gmbh Belt-and-pulley-type continuously variable transmission
JP2021008909A (ja) * 2019-06-28 2021-01-28 ダイハツ工業株式会社 締付対象物の共回り抑制構造

Also Published As

Publication number Publication date
EP0994275B1 (fr) 2003-09-24
DE69818466T2 (de) 2004-07-22
DE69818466D1 (de) 2003-10-30

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